Method for air-conditioning of environments in the marine field

ABSTRACT

A method for air-conditioning of watercraft and the like using a device with: an electronically controlled variable-r.p.m. compressor, a main gas/water condenser ( 5 ), at least one environmental heat-exchanger ( 3 ) with an electronically controlled fan ( 14 ), at least one electronically controlled expansion valve ( 8 ), and at least one first electronic control unit ( 4 ) programmed for calculating continuously a temperature deviation detected (DeltaT=T_ad−T_a), and as a function of said temperature deviation regulating in combination, the r.p.m. of the compressor ( 1 ), opening of the flow valve ( 8 ), and the r.p.m. of the fan of the heat-exchanger ( 3 ).

TECHNICAL SECTOR

The present invention relates to an air-conditioning system, and more inparticular a system for air-conditioning environments of ships, yachts,watercraft, etc., and in general environments that are located in themarine field, such as for example off-shore platforms.\

Currently, systems are known for conditioning nautical environments ofthe “ON/OFF” type, i.e., systems that are either on or off.

The basic features of these systems are:

-   -   just one available power;    -   temperature of the conditioned environment varying by at least        +/−3° C. with respect to the temperature setpoint (in optimal        conditions of arrangement of the diffusers);    -   ambient temperature varying continuously given that the        thermostat operates at intervals, with on/off machine cycles;        and    -   slow reaching of temperature setpoint.

This operating mode provides a rather approximate environmentaltemperature regulation: when the system is activated it introduces intothe environment to be conditioned air at a certain fixed temperature(10° C.), with a considerable difference with respect to the airpresent. When the temperature is reached, the system switches off (OFF)and resumes operation when the temperature sensors detect a temperaturehigher than a certain assigned value.

This determines a sawtooth timeplot of the temperature, with temperaturevariations that are considerable (+/−4° C.) for the people present inthe environment (non-optimal regulation). Furthermore, the air isintroduced into the environment at a temperature that is very differentfrom the one present with possible even situations of considerablediscomfort for the people present in the proximity of the air diffuser.

Furthermore, ON/OFF systems are unable to supply air at a differenttemperature in the various air-conditioned environments other than withpurely empirical systems. In a boat there frequently occur in factenvironmental situations that are differ considerably from one level toanother: for example, in summer, on the upper decks that are subjectedto the action of heating due to sunlight, there is a situation of muchhigher temperature than on the lower decks, which are partially immersedin the water, with a thermal difference of approximately 20° C. Sinceair at the same temperature is sent into the two environments, therearise situations of discomfort in one or the other and any compromise inany case represents a non-optimal situation.

From the patent application No. VA2010A00049, filed in the name of thepresent applicant, there is moreover known an air-conditioning systemprovided with electronic control designed to carry out regulation of aninverter compressor in order to maintain the ambient temperatureconstant or even to adapt it to the requirements of the people present.

However, it has been found that systems of a known type present somelimits as regards their efficiency and hence the possibility of beingable to air-condition environments of large dimensions or inunfavourable climatic or weather conditions by keeping the energy demandrelatively low.

The above drawback is particularly felt in the nautical field where itis desirable to have on board apparatuses of small dimensions and with alimited energy consumption.

PURPOSE OF THE INVENTION

Consequently, a first purpose of the present invention is to devise anair-conditioning apparatus for watercraft and the like that willovercome the drawbacks of systems of a known type.

SUMMARY OF THE INVENTION

The above purposes have been achieved with an apparatus according to atleast one of the annexed claims.

A first advantage lies basically in the fact that the apparatus enablescontrol of the current values of the parameters that are significant forthe purposes of energy efficiency, such as the power supplied, thelatent power, and the sensible power, and the system is capable ofoperating always substantially in conditions of maximum efficiency,without penalizing the rapidity in reaching the conditions oftemperature set by the user.

A further advantage lies in the possibility of using compressors oflower electric power and cubic capacity as compared to traditionalsystems, albeit reaching the same thermal power.

A further advantage is represented by the fact it becomes possible toprovide air-conditioning apparatuses of smaller dimensions as comparedto traditional ones.

LIST OF THE DRAWINGS

The above and further advantages will be better understood by any personskilled in the branch from the ensuing description and from the annexeddrawings, which are provided purely by way of non-limiting example andin which:

FIG. 1 is a schematic illustration of a first embodiment of theapparatus according to the invention;

FIG. 2 is a schematic illustration of a second embodiment of theapparatus according to the invention;

FIG. 3 is a schematic illustration of a third embodiment of theapparatus according to the invention;

FIG. 4 is a schematic illustration of a fourth embodiment of theapparatus according to the invention;

FIGS. 5-9 show some operating curves of the apparatus according to theinvention,

FIG. 10 is a schematic illustration of a water/gas heat-exchangeraccording to the invention;

FIG. 10A shows a stretch of piping of a heat-exchanger according to FIG.10;

FIG. 11 is a schematic illustration of possible management and controlinterfaces of an apparatus according to the invention.

DETAILED DESCRIPTION OF THE INVENTION

With reference to the attached drawings, an apparatus A forair-conditioning of watercraft and the like, in particular ships andyachts, is now described.

The apparatus comprises a variable-r.p.m. compressor 1, preferably anelectronically controlled inverter compressor for compression of a massof a phase-change working fluid.

The fluid is supplied by a line 10 of fluid in the gaseous phase to thecompressor, said line communicating with a duct 19 for outlet ofcompressed gas, which gives out into in an electronically controlledfour-way valve 9 in communication also with said gas line 10 at inlet tosaid compressor 1 and with a main gas/water condenser 5 via a gas duct23.

The condenser moreover communicates with a line 11 of fluid in theliquid phase and is traversed by a duct 18 for passage of a flow ofseawater moved by a purposely provided seawater-suction pump of theelectronically controlled variable-r.p.m. type.

Provided along the line 11 is at least one electronically controlledflow valve 8 intermediate with respect to at least one environmentalheat-exchanger 3 of the type comprising one or moreevaporation/condensation batteries for thermal conditioning of a flow ofair emitted by an electronically controlled fan 14, which at the otherend communicate with the line 10 of fluid in the gaseous phase.

According to the invention, in the embodiment illustrated in FIG. 1 theheat-exchanger 3 is provided with evaporation/condensation batteriescomprised in a water/gas heat-exchanger 15 associated to a fancoil viawater delivery and return lines 17, 28.

In the embodiment illustrated in FIG. 2, the heat-exchanger 3 isprovided, instead, with evaporation/condensation thermal batteries 16comprised in an air evaporator 16 associated to a fan.

Finally, illustrated in FIG. 3 is a configuration of the apparatus withheat exchangers of a split type, each associated to an environment to beair-conditioned and provided with respective evaporation/condensationthermal batteries 13.

The apparatus further comprises a distribution of temperature sensors,namely:

-   -   a first temperature sensor ST1 and a second temperature sensor        ST2 for detection of the temperature of the gas Tg_in, Tg_out at        inlet to and outlet from said compressor 1, respectively;    -   sensors ST5 and ST6 for instantaneous reading, respectively, of        the ambient temperature of the air T_a and of the conditioned        air at outlet from the heat-exchanger 3;    -   sensors ST7, ST8 for instantaneous reading of the surface        temperature of the ducts of the gas line 10 and liquid line 11,        respectively,—said ducts being made of thermally conductive        material, for example copper—for calculation of the latent        power;    -   pressure sensors SP10, SP11 associated to the sensors ST7 and        ST8 for calculation of the sensible power of the working coolant        in the gas and liquid lines, respectively;    -   sensors ST9, ST10 for instantaneous reading of the temperature        of the working fluid upstream and downstream, respectively, of        the condenser 5; and    -   means, preferably of the touch-screen type, for entering a        desired ambient temperature T_ad;

The apparatus is moreover provided with at least one first electroniccontrol unit 4, which receives the temperature values from the sensorsand from the input means referred to above, and is programmed forcontrolling at least:

-   -   r.p.m. of the compressor 1 and hence the power introduced into        the system;    -   opening of the flow valve 8 and hence the conditions of        expansion of the fluid;    -   r.p.m. of the fan 14 of the heat-exchanger 3 and hence the        degree of disposal of thermal power through the heat-exchanger;        and    -   r.p.m. of the variable-r.p.m. pump 6 and hence the degree of the        disposal of thermal power through the condenser 5.

According to the invention, the first electronic control unit 4calculates continuously a detected temperature deviationDeltaT=T_ad−T_a, and as a function of said temperature deviationregulates in combination:

-   -   r.p.m. of the compressor 1 on the basis of a pre-set operating        curve, represented by way of example in FIG. 5, so as to obtain        and maintain an output temperature of the compressed gas T_out        associated to the detected value of the temperature deviation        DeltaT; appearing on the abscissae in the graph of FIG. 5 is the        deviation DeltaT between ambient temperature T_a and temperature        setpoint T_ad and on the ordinates the temperature T of        evaporation of the gas on the line 10 that the compressor will        have to maintain in the conditioning step; the pressure and        temperature probe SP10 reads the current pressure and        accelerates the motor until the pre-set value is reached;        appearing, instead, in FIG. 9 is the qualitative curve, in        acceleration, deceleration, and maintenance, that links the        deviation DeltaT between the current ambient temperature T_a and        the temperature setpoint T_ad with the values read by ST7-ST8,        i.e., the temperatures at input to and output from the heat        exchangers 3; these values, together with the values of SP10 and        SP11 and of ST6 enable calculation of sensible power, latent        power, and total power; the result of the energy produced will        be confirmed by the reading on ST6; namely:        -   in acceleration of the compressor, to reach the set point            the control unit checks on the heat exchangers 3 whether the            latent power PL is higher than a certain percentage, for            example 5%, of the sensible power PS, and consequently the            r.p.m. of the compressor 1 decreases because it is producing            more heat than the heat-exchanger 3 can manage to dissipate;        -   in a deceleration step, the power demand on the compressor            is equal to the calculated power minus the latent power,            with recovery of the excess power;        -   in maintenance at setpoint, regulation causes the sensible            power and the latent power to coincide with dissipation of            all the energy produced;    -   opening of the flow valve 8 for maintaining a desired optimal        value of the temperature of the working fluid in the        heat-exchanger 3; qualitatively illustrated in FIG. 6 are the        curves of regulation of the solenoid valve 8 in the various        steps where the desired value of the ambient temperature (i.e.,        the setpoint T_ad) is reached, after said value has been        reached, and during maintenance of said value; advantageously,        the unit 4 can be programmed for controlling opening of the        valve 8 so that it will generate a variable working temperature        via the fan coil or water heat-exchange plate 3 according to the        thermal load of the system, or else, alternatively, so as to        keep the fan coil or heat-exchange plate 3 at fixed temperature,        regulating, however, the delivery of thermal power and the flow        of the coolant by means of the inverter compressor 1, in a        progressive way directly proportional to the r.p.m. of the        compressor.    -   r.p.m. of the fan of the heat-exchanger 3 to maintain a pre-set        optimal value of the temperature of evaporation/condensation of        the gas in the evaporation/condensation thermal batteries 13 for        the purposes of efficiency of the thermal cycle; for example, in        the case of use of working fluid of the R410A type, values of        from 0° C. to +7° C. will be used in evaporation, and values of        from 40° C. to 50° C. will be used in condensation; appearing in        FIG. 7 is a qualitative curve from which it may be seen that the        control unit applies a “software brake” to the fan if the        temperature T of the gas at outlet from the        evaporation/condensation thermal batteries is not at the optimal        value; the brake is greater the higher the temperature        deviation; advantageously, thanks to the invention electronic        management of the r.p.m. of the fan 14 prevents the temperature        of the gas from going beyond the pre-set parameters, which would        lead to higher consumption and lower thermal yield; by way of        example, if the user via the data-input means 12 sets a        temperature considerably far from the ambient temperature and        sets the fan manually to the maximum r.p.m., for some instants        the electronically controlled fan will not function at the        maximum r.p.m. until the battery 13 is filled properly and a        temperature of outgoing gas at the desired value is detected; at        this point, the fan will be accelerated and can operate at the        maximum r.p.m.; in the case where optimal filling of the battery        is lost, the fan will again be slowed down to enable the right        working point to be reached again, without requiring excessive        energy from the compressor; the system calibrated according to        the fluid used will optimize evaporation and condensation of the        gas at the optimal value so as to require as little mechanical        energy as possible, affording maximum chemical and thermal        yield; and    -   r.p.m. of the pump 6 as a function of a pre-set optimal value of        the temperature of the gas in the condenser 5 for the purposes        of efficiency of the thermal cycle; for example, appearing in        FIG. 8 is a qualitative curve from which it may be seen that the        r.p.m. of the pump increases as the deviation between the        optimal temperature and the detected temperature increases.

The apparatus can operate both as air-conditioning system, i.e., forcooling environments, and as heat pump for regulating heating of thewatercraft.

In a possible example of use of the apparatus, regulation is obtained asdescribed hereinafter.

Upon turning-on of the apparatus, the unit 4 reads the temperaturedeviation and hence the thermal power demand of the user and regulatesthe r.p.m. of the compressor 1, opening of the valve 8, the r.p.m. ofthe fan 14, and the r.p.m. of the pump 6 on the basis of the pre-setcurves appearing qualitatively in FIGS. 5-9.

As may be seen, to high values of temperature deviation DeltaT thereinitially corresponds a relatively high value of the r.p.m. of thecompressor and a low value of the r.p.m. of the fan so as to bring thetemperature of the gas T10 rapidly to the optimal value and obtain arapid filling of the evaporation/condensation thermal batteries 13 inconditions of maximum efficiency.

With progressive filling of the evaporation/condensation thermalbatteries 13, the fan may reach the maximum r.p.m., and thus also thecompressor will reach its maximum r.p.m. (if necessary) to be able todeliver the maximum power in order to reach the ambient-temperaturesetpoint T_ad rapidly. Advantageously, waiting for proper filling of thebattery in optimal working conditions enables the compressor to work inbetter conditions so reducing considerably consumption, roughly by 30%as compared to known systems.

When the ambient setpoint T_ad is reached, the r.p.m. of the compressoris reduced down to a maintenance value, and so also the r.p.m. of thefan 14 will be reduced according to the maintenance curve.

In the air-conditioning mode, the water pump 6 is regulated by thecontrol unit so that, in any circumstance, on the line 11 a constant andoptimal temperature is maintained for the type of fluid used. In theheating mode, the pump 6 is instead regulated for maintaining atconstant temperature, in the heat-exchanger 5, evaporation of the gasthat has to be drawn in by the compressor. Advantageously, with thisregulation of the water pump 6 it is possible to use seawater attemperatures of down to −15° C., as against the much higher limit oftemperature, roughly 7° C., below which in traditional systems it isnecessary use heating sources, such as boilers and the like.

Advantageously, thanks to the invention heat-exchange in the condenser 5occurs at a constant and defined temperature, and it is thus possible toobtain a complete liquefaction of the gas leaving the heat-exchanger,without any gas bubbles and hence with the possibility of working in anoptimal way in the cooling cycle thus obtaining maximum efficiency fromthe condensation process. Under-cooling can be managed and variedelectronically via control of the flow of water by means of theexpansion valve 8 set at the outlet of the condenser or else viasimultaneous management of partialization of the electronicallycontrolled expansion valves 2 (FIG. 3) set on the heat exchangers 3installed on the system.

According to the preferred embodiment illustrated, regulation of theelectronically controlled components of the apparatus, i.e., thecompressor 1, the condenser 5 with the pump 6, the heat-exchanger 3 withthe fan 14, the four-way valve 9, the expansion valve 8 and/or theexpansion valve 2, is obtained in combination in order to optimizethermal efficiency of the system as a whole. It is understood, however,that specific technical advantages are obtained thanks to the inventionalso by means of individual regulation of one or more of saidcomponents, which are provided with connection to an electronic controlunit and with sensors for detecting the state (temperature and/orpressure) of the working fluid set upstream and downstream of thecomponent itself.

Illustrated schematically in FIG. 3 is a configuration of the apparatuswith a plurality of heat exchangers 3 associated to a respectiveenvironment, each of which comprises a second electronic control unit 7,connected to the first control unit 4, preferably via a two-wire digitaldata line 68, for example of an RS485 Modbus or CANbus type.

In this configuration, the second electronic control units 7 regulatethe fans 14 of the various heat exchangers 3 and are connected both tothe means 12 for input of a desired ambient temperature and to thesensor ST5 for detecting the temperature of the associated environmentin order to calculate the specific temperature deviation DeltaT of eachenvironment.

Each heat-exchanger 3 further comprises an electronically controlledexpansion valve 2, regulated by the corresponding unit 7 and set alongthe liquid line 11. Advantageously, the second electronic control units7 are programmed for regulating in combination the r.p.m. of the fan 14and opening of the expansion valve 2 for maintaining the pre-set optimalvalue of the temperature of evaporation/condensation of the gas in theevaporation/condensation thermal batteries 13.

Illustrated with reference to FIG. 4 is an embodiment of the apparatuscomprising means 20, 21 operatively connected to the control unit 4,which are able to select one or more condensation circuits of smaller orgreater length, in direct proportion to the corresponding lower orhigher operating regimes of the compressor 1, in order to regulate thevolume of working fluid that circulates in the apparatus.

In a preferred example of embodiment, the regulating means 20, 21comprise an auxiliary condenser 50 set in parallel to the main condenser5 via a partialization valve 20 and a backup reservoir 21, which isconnected, via electronically controlled valves 24, 25, 26, upstream ofthe compressor 1, to the gas line 10 downstream of the four-way valve 9and to the liquid line 11 downstream of the flow valve 8.

Advantageously, with this solution it is possible, at start-up of theapparatus, to reduce considerably the mass of working fluid, for exampleby 50%, and manage to cool the gas in circulation in a short time.

When the temperature of the coolant on the lines 10 and 11 has anoptimal value, the compression rate is relatively modest, and the systemstarts to take in again the working fluid with sequential injections onthe intake line 10 and on the intake line upstream of the compressor 1.

The embodiment illustrated in FIG. 4 is particularly advantageous whenthe apparatus operates as heat pump, for example when it has to heatwatercraft in Pole seawaters.

In these conditions, on account of the very cold climate, thetemperature of return of the liquid gas on the line 11 towards thecondenser 5/50 will in fact be very low and hence at a low pressure,which in a traditional system would entail the need to use an oversizedcondenser, with consequent higher production costs and encumbrance.

According to the invention, instead, the control unit is programmed forinjecting gas at intake to the compressor when a low working temperatureand low working pressure are detected.

In this way, given the same r.p.m. of the compressor a higher intakepressure is obtained, with a higher pressure of discharge of thecompressor that will lead to a higher temperature of the delivery gas atinlet to the heat-exchanger.

Likewise, in apparatuses that envisage a large number of heatexchangers, the control logic envisages that there is instantaneouscharging of gas in order to optimize operation of the compressor and ofthe condenser according to the number of the fan coils active and theirthermal load.

In a further preferred embodiment, the apparatus may comprise infraredenvironmental sensors 27 connected to the control unit 4 or to thesecond electronic control units 7 for detecting the presence of one ormore persons present in the environment to be air-conditioned and foraccordingly regulating the apparatus on the basis of the thermal powerrequired for air-conditioning.

Furthermore, it is envisaged that the apparatus can be managed viaremote control means 62 connected to the electronic control units 4/7 bymeans of wireless communication networks, such as GSM, UMTS, or WI-FInetworks.

In a further preferred embodiment, the apparatus according to theinvention enables the user to set, either from a touch screen 64 or someother interface, maximum consumption of electricity of the system, forexample from 20% to 100% of the power that can be delivered. This isobtained with a dedicated software that controls the maximum r.p.m. ofthe inverter compressor 1 and the pressure of discharge (orcondensation) of the compressor by means of a pressure probe and atemperature probe, thus determining electrical consumption in advance.

In yet a further preferred embodiment, setting of the consumption can becontrolled also by means of a domotic system 61, possibly communicatingwith a remote terminal 62, which is connected to the control units 4/7for managing simultaneity or otherwise of the loads 63 required in theenvironments inside the watercraft in order to optimize the load of anumber of generators. For instance, if an electrical device, such as amicrowave oven, is turned on, the apparatus A can be controlled by thedomotic system 61 to reduce automatically absorption of theair-conditioning apparatus for a few minutes and then restore it whenthe device is turned off.

Illustrated in FIG. 10 is a preferred embodiment of a heat-exchanger 60according to the invention, comprising a tube-nest heat-exchange unit30, set between a line 23 of flow of working fluid in the gaseous phasefor connection to a compressor and a line 11 of flow of working fluid inthe liquid phase, set in a relation of heat-exchange with a flow ofwater forced by a pump 6 and coming from a source 18, constituted forexample by seawater.

The heat-exchanger further comprises an electronically regulated flowvalve 8, set along the liquid line 11, and at least one sensor 32 fordetecting the temperature of condensation/evaporation of the workingfluid, and an electronically controlled water pump 6 for regulating theflow rate of the water coming from the source 18.

According to the invention, the heat-exchanger is provided with anelectronic control unit 40 operatively connected to the sensor 32, tothe valve 8, and to the pump 6 for regulating the flow of coolant and ofwater on the basis of a difference of temperature between thetemperature detected and a desired optimal temperature ofcondensation/evaporation of the working fluid.

Preferably, the heat-exchanger 60 further comprises means 33, 34 (setinside and/or outside the heat-exchanger) for storage of an amount ofworking fluid treated and condensed at the desired temperature in orderto create a thermal flywheel that will optimize operation of thecompressor and reduce energy consumption.

In a preferred embodiment, the tubes 65 that constitute the unit 30 andthrough which the coolant gas is made to pass within the heat-exchangerare made of titanium and have a coiled shape (for example, the shape ofa coil wound along the longitudinal axis a with one turn 66 percentimetre of length) to offer a larger heat-exchange surface and toincrease in a controlled way the turbulence of the gas inside in orderto increase efficiency of the heat-exchanger and reduce the overalldimensions thereof.

The invention has been described with reference to a preferredembodiment. Equivalent elements may be used, without thereby departingfrom the sphere of protection or scope of the patent right granted.

The invention claimed is:
 1. A method for air-conditioning of watercraftby means of an on-board apparatus of the type comprising: anelectronically controlled variable-r.p.m. compressor (1) for compressionof a mass of a phase-change working fluid, supplied by a line (10) offluid in the gaseous phase and communicating with a duct (19) for outletof a flow of the fluid in the form of compressed gas; a heat exchangesource constituted of seawater; a main gas/water condenser (5, 60)communicating with a duct (23) carrying fluid in the gaseous phase, witha duct for passage of a flow of water (18) delivered by a purposelyprovided electronically controlled variable-r.p.m. seawater suction pump(6), and with a line (11) of fluid in the liquid phase; at least oneenvironmental heat-exchanger (3) comprising one or moreevaporation/condensation thermal batteries (13) communicating with saidline (11) of working fluid in the liquid phase and with said line (10)of working fluid in the gaseous phase, and provided withevaporation/condensation thermal batteries (13) (13, 15, 16) for thermalconditioning of a flow of air emitted by an electronically controlledfan (14); an electronically controlled four-way valve (9) incommunication with said gas line (10), with the inlet and the outlet ofsaid compressor (1), and with said condenser (5); at least oneelectronically controlled flow valve (8) set along said line (11) ofworking fluid in the liquid phase; a first temperature sensor (ST1) anda second temperature sensor (ST2) for detection of the temperature ofthe gas (Tg_in; Tg_out) at inlet to and outlet from said compressor (1),respectively: a temperature and/or pressure sensor (ST8/SP11), fordetection of the conditions of the working fluid in the liquid phase inthe line (11); a temperature and/or pressure sensor (ST7/SP10), fordetection of the conditions of the working fluid in the gaseous phase inthe line (10); a fifth sensor (ST5) for detection of the temperature ofsaid environment (T_a); means (12) for entering a desired ambienttemperature (T_ad); and at least one first programmable electroniccontrol unit (4) operatively connected to: said compressor (1); saidflow valve (8); said sensors (ST1, ST2) for detecting the temperature ofthe gas (Tg_in; Tg_out) at inlet to and outlet from said compressor,respectively; a first sensor (SP11) for detecting the pressure of thefluid in said liquid line (11); a second sensor (SP10) for detecting thepressure of the fluid in said gas line (10); said fifth sensor (ST5) fordetecting the ambient temperature; said fan (14) of the heat-exchanger(3); said input means (12) for entering a desired ambient temperature(T_ad), and said seawater suction pump, wherein said first control unit(4) continuously calculates a temperature deviation detected(DeltaT=T_ad−T_a), and as a function of said temperature deviationregulates in combination: the r.p.m. of the compressor (1) on the basisof a pre-set operating curve for obtaining an output temperature of thecompressed gas (T_out) associated to the detected value of saidtemperature deviation (DeltaT); opening of the flow valve (8) formaintaining a desired optimal value of the temperature of the gasarriving at the heat-exchanger (3); and the r.p.m. of the fan of theheat-exchanger (3) for maintaining a pre-set optimal value of thetemperature of evaporation/condensation of the gas in theevaporation/condensation thermal batteries (13) for the purposes ofefficiency of the thermal cycle; the method for air-conditioningcomprising: acceleration of the compressor (1) by said control unit (4),wherein said control unit (4) is programmed for controlling whether thelatent heat to the heat exchangers (3) is greater than a givenpercentage of the sensible heat and in this case reducing accordinglythe r.p.m. of the compressor (1); deceleration of the compressor (1) bysaid control unit (4), wherein said control unit (4) is programmed torequire of the compressor a power substantially equal to the differencebetween a calculated power and the latent heat; and maintenance of thedesired ambient temperature by said control unit (4), wherein saidcontrol unit (4) is programmed so that the sum of the sensible heat andof the latent heat substantially coincides with the dissipated energyproduced.
 2. The method according to claim 1, wherein at least onesecond electronic control unit (7) is provided, the second electroniccontrol unit (7) being associated to said environmental heat-exchanger(3) and operatively connected to said first control unit (4), to saidfan (14) of the heat-exchanger (3), to said sensor (ST5) for detectingthe ambient temperature, and to said means (12) for entering a desiredambient temperature (T_ad), the second electronic control unit (7)carrying out continuous calculation of the temperature deviationdetected (DeltaT=T_ad−T_a) and, on the basis of the latter, to managethe instantaneous power demand, an electronically controlled expansionvalve (2) set along said line (11) of fluid in the liquid phase andassociated to said environmental heat-exchanger (3) is provided; whereinsaid second electronic control unit (7) is programmed for regulating incombination the r.p.m. of the fan (14) of the heat-exchanger (3) andopening of the expansion valve (2) in order to maintain a pre-setoptimal value of the temperature of evaporation/condensation of the gasin the evaporation/condensation thermal batteries (13) for the purposesof efficiency of the thermal cycle, and reach more rapidly the value ofthe ambient temperature set.
 3. The method according to claim 1,comprising means (20) operatively connected to said control unit (4)that are able to select one or more condensation circuits (5, 50) ofsmaller or greater length, in direct proportion to corresponding loweror higher operating regimes of the compressor (1 in order to regulatethe volume of working fluid that circulates in the apparatus.
 4. Themethod according to claim 1, wherein said evaporation/condensationthermal batteries are comprised in a water/gas heat-exchanger (15)associated to a fancoil via lines (17, 28) for delivery and return ofwater.
 5. The method according to claim 1, wherein saidevaporation/condensation thermal batteries are comprised in a water/gasheat-exchanger (15) or in an air evaporator (16) associated to a fan. 6.The method according to claim 3, further comprising regulating thevolume of working fluid that circulates in the apparatus using aregulating means (20, 21) comprising: an auxiliary condenser (50) set inparallel to the main condenser (5) via a partialization valve (20); anda backup reservoir (21) connected, via electronically controlled valves(24, 25, 26) upstream of the compressor (1), to the gas line (10)downstream of the four-way valve (9) and to the liquid line (11)downstream of the flow valve (8).
 7. The method according to claim 1,wherein infrared environmental sensors operatively connected to one ofsaid control units (4, 7) are provided for detecting the presence of oneor more persons in the environment to be air-conditioned and accordinglyregulating the compressor (1).
 8. The method according to claim 1,wherein a wireless remote terminal is provided, operatively connected toone of said electronic control units (4, 7) by means of wirelesscommunication networks, such as GSM, UMTS, or Wi-Fi networks.
 9. Themethod according to claim 1, wherein said means (12) for entering adesired ambient temperature comprise a display of the touch-screen type.10. The method according to claim 2, wherein said first and secondcontrol units (4, 7) are connected via a two-wire digital data line(68).